CN112128104A

CN112128104A - Rotary compressor and refrigeration cycle system

Info

Publication number: CN112128104A
Application number: CN202010859522.2A
Authority: CN
Inventors: 小津政雄; 王玲
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2020-08-24
Filing date: 2020-08-24
Publication date: 2020-12-25
Anticipated expiration: 2040-08-24
Also published as: CN112128104B

Abstract

The invention discloses a rotary compressor and a refrigeration cycle system, the rotary compressor comprises a shell, a motor, a compression mechanism and a low-pressure pipeline, the motor is arranged in the shell and is provided with a crankshaft, the compression mechanism is arranged in the shell and is driven by the crankshaft, the compression mechanism comprises an air cylinder, a piston, a sliding sheet and a sliding sheet control device, the air cylinder is internally provided with a cylinder chamber and a sliding sheet groove, the piston eccentrically rotates in the cylinder chamber, the sliding sheet can reciprocate in the sliding sheet groove, the sliding sheet control device is connected with the low-pressure pipeline, one end of the sliding sheet control device extends into the cylinder chamber and can reciprocate between a first position and a second position according to the pressure difference delta P between the shell and the low-pressure pipeline, the sliding sheet control device presses the sliding sheet towards the piston to enable the sliding sheet to press the peripheral surface of the piston, and the sliding sheet control device releases the pressing of the piston at the second. The sliding vane control device of the rotary compressor is not easy to damage, has high compression efficiency, long service life and low operation noise.

Description

Rotary compressor and refrigeration cycle system

Technical Field

The invention belongs to the technical field of compressors, and particularly relates to a rotary compressor and a refrigeration cycle system.

Background

A rotary compressor generally includes a casing, a motor assembly, and a compression mechanism, in which a vane of the compression mechanism is a main component of the rotary compressor, abuts against an outer circumference of a piston rotatable in a compression chamber and reciprocates to compress suction gas sucked in a cylinder into compressed gas.

Disclosure of Invention

The present invention is based on the discovery and recognition by the inventors of the following facts and problems:

in the related art, in order to increase the pressure after the rotary compressor is started, a spring for pressing the vane needs to be provided at the rear end of the vane. The inventors have found that, after the rotary compressor is started and pressure is increased, it is not necessary to press the vane with a spring, but it is very difficult to automatically stop the spring that is operating. In addition, with the development of miniaturization and high speed of the rotary compressor, the spring of the slide piece starting to move reciprocates between the start of the rotary compressor and the stop of the rotary compressor, and when the rotary compressor is operated at high speed, the spring is easily damaged, the efficiency of the rotary compressor is low, the noise is large, and the like.

To this end, an embodiment of an aspect of the present invention proposes a rotary compressor which does not cause a problem of damage of a spring even when operated at a high speed, has high reliability, and improves compression efficiency.

An embodiment of another aspect of the present invention is directed to a refrigeration cycle system.

A rotary compressor according to an embodiment of a first aspect of the present invention includes a casing, a motor provided in the casing and having a crankshaft, a compression mechanism provided in the casing and driven by the crankshaft, and a low-pressure line, the compression mechanism including: the air cylinder is internally provided with a cylinder chamber and a slide sheet groove; a piston eccentrically rotating within the cylinder chamber; the sliding sheet can move in a reciprocating manner in the sliding sheet groove; the slip sheet control device is connected with the low-pressure pipeline, one end of the slip sheet control device extends into the cylinder chamber and can move back and forth between a first position and a second position according to the pressure difference delta P between the interior of the shell and the interior of the low-pressure pipeline, the slip sheet control device faces the piston and presses the slip sheet so that the slip sheet presses the outer peripheral face of the piston, and the slip sheet control device releases the pressing of the slip sheet on the piston at the second position.

According to the rotary compressor provided by the embodiment of the invention, the slip sheet control device connected with the low-pressure pipeline is arranged, one end of the slip sheet control device extends into the cylinder chamber and can reciprocate between the first position and the second position according to the pressure difference delta P between the shell and the low-pressure pipeline, and when the rotary compressor runs, the pressure difference delta P is utilized to drive the slip sheet control device to be separated from the slip sheet, so that the slip sheet control device does not reciprocate along with the high-speed rotation of the piston, the damage of the slip sheet control device caused by high-frequency expansion is avoided, and the reliability and the compression efficiency of the rotary compressor are improved.

In some embodiments, the slide control device is in the first position when the pressure difference Δ P is 0; and when the pressure difference delta P is larger than or equal to K, the slide sheet control device is at the second position, wherein K is larger than 0 and is a preset pressure within a preset time after the compression assembly is started.

In some embodiments, K is a preset pressure within 30s after the compression assembly is activated.

In some embodiments, a cross hole is provided in a block of the cylinder, the cross hole communicating with the cylinder chamber, and the vane control device includes: the cylinder body part is internally provided with a cavity, the cylinder body part is connected with the machine shell, the cylinder chamber loop is communicated with the cavity, and the cavity is communicated with the transverse hole; the valve body is arranged in the cavity and can move in the cavity along the length direction of the barrel part; one end of the central shaft is connected with the valve body, and the other end of the central shaft penetrates through the cylinder body of the air cylinder through the transverse hole to be in contact with and far away from the sliding sheet; the elastic piece is arranged in the cavity, one end of the elastic piece is connected with the valve body, the other end of the elastic piece is connected with the inner wall surface of the cylinder piece, and the elastic piece has elastic force which presses the valve body towards the piston.

In some embodiments, a first end of the cylinder member is open such that one end of the cavity is open, the first end of the cylinder member is connected to the cylinder block of the cylinder through the casing, and one end of the low pressure line is communicated with the cavity through a second end of the cylinder member.

In some embodiments, the outer peripheral surface of the barrel member is provided with an annular boss adjacent to the first end of the barrel member, the annular boss includes a first end surface and a second end surface oppositely arranged in the length direction of the barrel member, the first end surface of the annular boss is adjacent to the first end of the barrel member than the second end surface, and the first end surface of the annular boss and the outer peripheral surface of the casing are fitted to each other.

In some embodiments, the other end of the central shaft has a conical tip, the conical tip having a cross-sectional area that gradually decreases in a direction away from the other end of the central shaft.

In some embodiments, the cross-section of the central shaft has a circumferential profile that is circular, the diameter of the central shaft being less than the width of the slide that can abut the central shaft.

In some embodiments, the crankshaft includes a first eccentric portion, a second eccentric portion, and a middle shaft connected between the first eccentric portion and the second eccentric portion, the cylinder includes a first cylinder and a second cylinder, the first cylinder has a first cylinder chamber and a first slide groove, the second cylinder has a second cylinder chamber and a second slide groove, a partition plate is disposed between the first cylinder and the second cylinder, the partition plate has a central cavity penetrating the partition plate in an axial direction of the crankshaft, the middle shaft is fitted in the central cavity, the piston includes a first piston and a second piston, the first eccentric portion is fitted in the first piston to drive the first piston to eccentrically rotate in the first cylinder chamber, the second eccentric portion is fitted in the second piston to drive the second piston to eccentrically rotate in the second cylinder chamber, and the slide plate includes a first slide plate and a second slide plate, the first sliding sheet can move in a reciprocating mode in the first sliding sheet groove, the second sliding sheet can move in a reciprocating mode in the second sliding sheet groove, one end of the sliding sheet control device stretches into the first cylinder chamber, the first sliding sheet can press the outer peripheral face of the first piston according to the pressure difference delta P, and the pressing of the first sliding sheet on the first piston can be relieved.

A refrigeration cycle system according to an embodiment of a second aspect of the present invention includes a compressor, a condenser, an expansion valve, an evaporator, and an accumulator, the compressor being the rotary compressor according to any one of the above embodiments, and a low-pressure line of the rotary compressor being connected to the accumulator.

According to the refrigeration cycle system provided by the embodiment of the invention, by adopting the rotary compressor, the system is stable in operation, high in compression efficiency and low in operation noise.

Drawings

Fig. 1 is a schematic view of a refrigeration cycle system according to an embodiment of the present invention.

Fig. 2 is a schematic structural view of a longitudinal section of a compression mechanism of the rotary compressor of fig. 1.

Fig. 3 is a schematic structural view of a cross section of a compression mechanism of the rotary compressor of fig. 1.

Fig. 4 is a structural schematic view and an assembly view of a vane control device of a rotary compressor according to an embodiment of the present invention.

Fig. 5 is a graph showing the changes over time of the casing pressure Pd and the low-pressure pipe pressure Ps during the period from the standstill to the steady operation after the start-up to the standstill of the rotary compressor according to the embodiment of the present invention.

Fig. 6 is a comparison diagram of states of the vane control device of the rotary compressor according to the embodiment of the present invention when Δ P is 0 and Δ P > 0.

Fig. 7 is a comparison diagram of states of a vane control device of a rotary compressor according to an embodiment of the present invention when Δ P > 0 and Δ P ═ K.

Fig. 8 is a state change diagram of a vane control device of a rotary compressor in a process from an operation to a stop of the rotary compressor according to an embodiment of the present invention.

Reference numerals:

the rotary compressor includes a rotary compressor 1A, a casing 2, an exhaust pipe 3, a motor 4, a compression mechanism 5, a partition plate 13, a first bearing 15, a second bearing 16, a first muffler 15B, a second muffler 16B, a low-pressure pipe 30A, a first intake pipe 7A, a second intake pipe 7B, a liquid reservoir 8, a first cylinder 10A, a first cylinder chamber 10A, a second cylinder 14B, a first vane 20A, a fitting groove 20A, a second vane 20B, a first piston 22A, a second piston 22B, a first vane groove 11B, a vane control device 30, a cylinder member 30A, a valve body 34, a center shaft 33, a conical end 33a, an elastic member 31, an annular boss 30B, a longitudinal hole 12A, a transverse hole 12B, a crankshaft 18, a first eccentric portion 18a, a second eccentric portion 18B, a condenser 40, an expansion valve 41, and an evaporator 43.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

A rotary compressor and a refrigeration cycle system according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

As shown in fig. 1 to 8, a rotary compressor 1A according to an embodiment of the present invention includes a casing 2, a motor 4, a compression mechanism 5, and a low pressure pipe 30 a.

The motor 4 is provided in the housing 2 and has a crankshaft 18. As shown in fig. 2, the motor 4 is fixed on the inner wall of the housing 2, and one end of the crankshaft 18 (the upper end of the crankshaft 18 in fig. 2) is inserted into the motor 4 and fixedly connected with the motor 4.

The compression mechanism 5 is provided in the casing 2 and is driven by a crankshaft 18 of the motor 4. As shown in fig. 2, the compressing mechanism 5 is fixed on the inner wall of the casing 2 and located below the motor 4, the other end of the crankshaft 18 (the lower end of the crankshaft 18 in fig. 2) is fixedly connected with the compressing mechanism 5, and the motor 4 drives the crankshaft 18 to rotate, thereby driving the compressing mechanism 5.

The compression mechanism 5 comprises a cylinder, a piston, a sliding sheet and a sliding sheet control device 30, wherein a cylinder chamber and a sliding sheet groove are arranged in the cylinder, and the piston eccentrically rotates in the cylinder chamber.

The vane is reciprocally movable (reciprocally movable in the inward and outward directions shown in fig. 2) in the vane groove, and a leading end portion (e.g., an inner end of the vane in fig. 2) of the vane is in contact with an outer circumferential surface of the piston to divide the cylinder chamber into a suction chamber and a compression chamber.

The slide control means 30 is connected to the low pressure line 30a, and one end of the slide control means 30 extends into the cylinder chamber and is reciprocally movable between a first position and a second position according to a pressure difference Δ P (i.e., a difference between Pd and Ps shown in fig. 4) between the inside of the casing 2 and the inside of the low pressure line 30 a. In the first position, the slide control device 30 presses the slide against the piston to press the slide against the outer circumferential surface of the piston, and in the second position, the slide control device 30 releases the pressing of the slide against the piston.

As shown in fig. 2, a cavity is provided in the sliding-vane control device 30, an outer end of the sliding-vane control device 30 is connected to the low-pressure pipeline 30a so that low-pressure gas enters the cavity, an inner end of the sliding-vane control device 30 can be in contact with and separated from an outer end of the sliding vane, the sliding vane can be pressed on the outer circumferential surface of the piston when the inner end of the sliding-vane control device 30 is in contact with the sliding vane, and when the sliding-vane control device 30 is separated from the sliding vane, no pressing force is provided between the sliding vane and.

The inventor of the present invention has found that after the rotary compressor is started and starts to increase the pressure, the spring is not needed to press the sliding vane, and in the rotary compressor in the related art, the sliding vane is always abutted against the outer circumferential surface of the piston by the spring, and the spring expands and contracts at a high frequency along with the high-speed rotation of the piston, which easily causes damage to the spring. Therefore, the inventor proposes a sliding vane control device to replace the spring, and in the technical scheme, the sliding vane control device can change the motion state according to the pressure difference delta P in the casing and the low-pressure pipeline so as to solve the problem of part strain caused by high-frequency reciprocating motion.

It can be understood that, as shown in fig. 6-r, in the rotary compressor which is not started up, the pressure difference Δ P between the inside of the casing 2 and the inside of the low pressure pipe 30a is equal to 0, the slide control device 30 moves inward under its own driving force to contact the slide and pushes the slide to press the slide against the outer circumferential surface of the piston, so that the compression mechanism 5 can start the suction and compression of the gas.

As shown in fig. 6-c, after the compressing mechanism 5 is started, the pressure difference Δ P between the inside of the casing 2 and the inside of the low pressure pipe 30a is greater than 0, and the pressure difference acts on the slide control device 30 and provides an outward moving force. With the increase of the operation time of the compressor, as shown in fig. 7-c, when Δ P is gradually increased, the force generated by the pressure difference may overcome the driving force of the sliding-vane control device 30 itself, so as to push the sliding-vane control device 30 to move outward to separate the sliding-vane control device 30 from the sliding vane, there is no pressing force between the sliding vane and the piston, and the sliding-vane control device 30 cannot be driven to move by the high-speed rotation of the piston. As shown in fig. 7 to ((r)), when Δ P increases to a certain value, the vane control device 30 is completely separated from the vane and always kept away from the vane.

In some embodiments, as shown in fig. 5 to 8, when the pressure difference Δ P is 0, the vane control device 30 is in the first position, that is, the vane control device 30 presses the vane to abut against the outer circumferential surface of the piston to divide the cylinder chamber into the suction chamber and the compression chamber, so that the compression mechanism 5 can suck and compress the gas.

When the pressure difference Δ P is greater than or equal to K, the sliding-vane control device 30 is at the second position, that is, the sliding-vane control device 30 is far away from the sliding vane, no pressing force exists between the sliding vane and the piston, and the piston cannot drive the sliding-vane control device 30 to reciprocate, wherein K is greater than 0 and is a preset pressure within a preset time after the compression mechanism 5 is started.

Specifically, after the compressor is started, as shown in fig. 5 and 6-c, the piston eccentrically rotates, the vane pressed by the vane control device 30 starts to reciprocate, the air pressure in the casing 2 rises, and Δ P increases. As shown in fig. 7- ((r)), when the pressure difference Δ P is K, the distance from the vane control device 30 to the vane is the largest. For example, as shown in fig. 5, when K is 0.3MPa, which is a preset design value, the timing at which the slide control device is disengaged from the slide can be determined by using the magnitude relationship between K and Δ P.

Further, as shown in fig. 5, as the operation time changes, Δ P increases, T becomes 15 minutes, the pressure stabilizes, Pd becomes 2.9MPa, Ps becomes 0.8MPa, and Δ P becomes 2.1, that is, the static state of the slide control device 30 in fig. 7-r is maintained. With further increase of the operation time, when T is 60 minutes, as shown in fig. 8-fifthly, the compression mechanism 5 stops operating, the air pressure in the casing 2 decreases, and Δ P starts to decrease until Δ P decreases to 0 as shown in fig. 8-sixthly, the slide sheet control device 30 presses the slide sheet to abut against the piston, one compression cycle of the compression mechanism 5 is completed, and the compression mechanism 5 can perform a new compression cycle.

Therefore, in the preset time after the rotary compression mechanism is started, the piston can rotate at a high speed, the size relation between delta P and K value is utilized, when the piston enters high-speed rotation, the slip sheet control device is controlled to be separated from the slip sheet, and the slip sheet control device is prevented from high-frequency contraction along with the high-speed rotation of the piston.

Preferably, as shown in fig. 5, K is a preset pressure within 30s after the compression assembly is activated.

In some embodiments, as shown in fig. 2 and 4, a cross hole 12b is provided in a cylinder body of the cylinder, the cross hole 12b communicates with the cylinder chamber, and the sliding vane control device 30 includes a cylinder member 30A, a valve body 34, a center shaft 33, and an elastic member 31.

Specifically, as shown in fig. 2 and 4, the cylinder member 30A has a cavity therein, the cylinder member 30A is connected to the housing 2, the cylinder chamber circuit communicates with the cavity, and the cavity communicates with the cross hole 12 b. As shown in fig. 2, the cylinder 30A passes through the housing 2 in the inside-outside direction, the horizontal hole 12b passes through the cylinder in the inside-outside direction, the cylinder is provided with a vertical hole 12a passing through the cylinder in the up-down direction, the horizontal hole 12b communicates with the vertical hole 12a, the inner end of the cylinder 30A communicates with the horizontal hole 12b, and the outer end of the cylinder 30A communicates with the cylinder loop (low pressure pipeline 30A), so that the pressure difference between the gas in the housing 2 and the gas in the cylinder loop can be formed in the cavity.

The valve body 34 is disposed in the cavity and is movable in the cavity in the longitudinal direction (the inside and outside direction shown in fig. 2) of the cylinder member 30A, one end of the center shaft 33 is connected to the valve body 34, and the other end of the center shaft 33 is contactable with and separable from the slide through the cylinder body of the cylinder via the cross hole 12 b. As shown in fig. 2 and 4, the outer end of the central shaft 33 extends into the cavity, the outer end of the central shaft 33 is connected to the valve body 34, the inner end of the central shaft 33 extends into the cylinder chamber through the transverse hole 12b, the inner end of the central shaft 33 is in contact with and separable from the outer end of the slide, and the cavity has a stroke C in the inner and outer directions, in which the valve body 34 can move.

The elastic member 31 is provided in the cavity, and one end of the elastic member 31 is connected to the valve body 34, and the other end of the elastic member 31 is connected to the inner wall surface of the cylindrical member 30A, and the elastic member 31 has an elastic force that presses the valve body 34 toward the piston. As shown in fig. 2, the inner end of the elastic member 31 is connected to the valve body 34, the outer end of the elastic member 31 is connected to the inner sidewall of the cylinder member 30A, and the elastic member 31 has an elastic force for pushing the valve body 34 to move toward the inside of the housing 2. Preferably, the elastic member 31 is a spring.

Further, a first end of the cylinder member 30A (an inner end of the cylinder member 30A in fig. 2) is opened so that one end of the cavity is opened, the first end of the cylinder member 30A is connected to the cylinder body of the cylinder through the casing 2, and one end of the low pressure pipe 30A is communicated with the cavity through a second end of the cylinder member 30A (an outer end of the cylinder member 30A in fig. 2).

Specifically, the valve body 34 may divide the cavity into two parts, the gas in the casing 2 is adapted to flow into the cavity part inside the valve body 34 through the inner end opening of the cavity, the low-pressure gas is adapted to flow into the cavity part outside the valve body 34, the pressure difference may act on the sidewall of the valve body 34, and when the pressure difference Δ P is greater than or equal to K, the pressure difference may push the valve body 34 to move outward (i.e., to move from the high-pressure direction to the low-pressure direction), so as to separate the sliding-vane control device 30 from the sliding vane.

In some embodiments, as shown in fig. 2 and 3, the outer circumferential surface of the cylinder member 30A is provided with an annular boss 30b, the annular boss 30b is adjacent to the first end of the cylinder member 30A, the annular boss 30b includes a first end surface and a second end surface which are oppositely arranged in the length direction of the cylinder member 30A, the first end surface of the annular boss 30b is adjacent to the first end of the cylinder member 30A compared with the second end surface, and the first end surface of the annular boss 30b and the outer circumferential surface of the casing 2 are attached to each other.

As shown in fig. 3, the outer peripheral face of the cylinder 30A is provided with an annular boss 30b which surrounds the outer periphery of the cylinder 30A and is close to the inner end of the cylinder 30A, the annular boss has a certain thickness in the inner and outer directions, and the inner side face of the annular boss 30b is attached to the outer peripheral face of the casing 2.

In some embodiments, as shown in fig. 3 and 4, the other end of the central shaft 33 has a conical tip 33a, and the cross-sectional area of the conical tip 33a gradually decreases in a direction away from the other end of the central shaft 33.

As shown in fig. 3 and 4, the cross-sectional area of the conical tip 33a is gradually reduced from the outside to the inside, and it can be understood that the outer circumferential surface of the conical tip 33a is an inclined arc-shaped surface, thereby facilitating the matching of the central shaft and the sliding vane when the central shaft contacts the sliding vane, reducing the contact friction, and reducing the operation noise of the rotary compressor.

Further, as shown in fig. 3, the outer peripheral profile of the cross section of the center shaft 33 is circular, and the diameter of the center shaft 33 is smaller than the width of the slide plate which can abut against the center shaft 33. Therefore, the slide plate is convenient to be provided with the matching groove 20a which can be matched with the end part of the central shaft 33, thereby improving the contact reliability and stability of the central shaft and the slide plate.

In some embodiments, as shown in fig. 2 and 3, the crankshaft 18 includes a first eccentric portion 18a, a second eccentric portion 18B, and an intermediate shaft connected between the first eccentric portion 18a and the second eccentric portion 18B, the cylinders include a first cylinder 10A and a second cylinder 14B, the first cylinder 10A has a first cylinder chamber 10A and a first vane groove 11B, the second cylinder 14B has a second cylinder chamber (not shown) and a second vane groove (not shown), a partition plate 13 is provided between the first cylinder 10A and the second cylinder 14B, the partition plate 13 is provided with a central cavity penetrating the partition plate 13 in an axial direction of the crankshaft 18, and the intermediate shaft is fitted in the central cavity.

In other words, the first cylinder 10A and the second cylinder 14B may be simultaneously operated to increase the operation efficiency of the compression mechanism 5, and in order to achieve the connection of the crankshaft 18 with the first cylinder 10A and the second cylinder 14B, the central cavity is adapted to be penetrated by the crankshaft 18 by providing the central cavity on the partition plate 13, so as to achieve the assembly of the crankshaft 18 with the first cylinder 10A, the partition plate 13, and the second cylinder 14B.

Specifically, as shown in fig. 2, the motor 4 is provided in the housing 2, the motor 4 has a crankshaft 18 extending in the up-down direction, the compression mechanism 5 is fixed to the inner peripheral surface of the housing 2, the outer peripheral wall of the crankshaft 18 is provided with a first eccentric portion 18a and a second eccentric portion 18b, the first eccentric portion 18a is located above the second eccentric portion 18b, and the first eccentric portion 18a and the second eccentric portion 18b are connected by an intermediate shaft.

The compression mechanism 5 is located below the motor 4, the first cylinder 10A and the second cylinder 14B are spaced apart in the up-down direction in the casing 2, the first cylinder 10A is located above the second cylinder 14B, the first cylinder 10A has a first vane groove 11B therein extending in the radial direction of the casing 2, and the second cylinder 14B has a second vane groove therein extending in the radial direction of the casing 2. The lower end of the crankshaft 18 sequentially passes through the first cylinder 10A, the partition plate 13 and the second cylinder 14B, a central cavity which is communicated up and down is arranged on the partition plate 13 corresponding to the crankshaft 18, and the intermediate shaft penetrates through the central cavity

The pistons include a first piston 22A and a second piston 22B, with a first eccentric portion 18a fitted within the first piston 22A to cause eccentric rotation of the first piston 22A within the first chamber 10a, and a second eccentric portion 18B fitted within the second piston 22B to cause eccentric rotation of the second piston 22B within the second chamber.

As shown in fig. 2, the first eccentric portion 18a is provided in the first piston 22A and is continuous with the inner peripheral surface of the first piston 22A, and the second eccentric portion 18B is provided in the second piston 22B and is continuous with the inner peripheral surface of the second piston 22B.

In some embodiments, as shown in fig. 2 and 3, the slide plate includes a first slide plate 20A and a second slide plate 20B, the first slide plate 20A is reciprocally movable in the first slide plate groove 11B, the second slide plate 20B is reciprocally movable in the second slide plate groove, one end of the slide plate control device 30 extends into the first cylinder chamber 10A and can enable the first slide plate 20A to press the outer circumferential surface of the first piston 22A and release the pressing of the first piston 22A by the first slide plate 20A according to the pressure difference Δ P.

The second vane 20B is stationary with the rotary compressor 1A stopped, and presses the second piston 22B. Further, similarly to the first slide 20A, when the pressing of the first slide 20A is released, the pressing of the second slide 20B is released at the same time.

As shown in fig. 3, the first vane groove 11b extends in the radial direction of the housing 2, the first vane 20A is accommodated in the first vane groove 11b, and the inner end of the first vane 20A is in contact with the outer peripheral surface of the first piston 22A to divide the first cylinder chamber 10A into a first suction chamber and a first compression chamber. A slidable space is provided between the outer end of the first slide piece 20A and the bottom wall of the first slide piece groove 11b, so that the first slide piece 20A can reciprocate in the first slide piece groove 11 b.

In some embodiments, as shown in fig. 2, the compression mechanism 5 further includes a first bearing 15 and a second bearing 16, the first bearing 15 and the second bearing 16 are both sleeved on the crankshaft 18, the first bearing 15 is connected to the upper surface of the first cylinder 10A to seal the compression cavity of the first cylinder 10A, and the second bearing 16 is connected to the lower surface of the second cylinder 14B to seal the compression cavity of the second cylinder 14B.

A refrigeration cycle system according to an embodiment of the present invention will be described with reference to fig. 1.

A refrigeration cycle system according to another aspect embodiment of the present invention includes a compressor which is a rotary compressor 1A according to an embodiment of the present invention, a condenser 40, an expansion valve 41, an evaporator 43, and an accumulator 8.

As shown in fig. 1, the top of the casing 2 is provided with an exhaust pipe 3, high-pressure gas is adapted to be discharged from the exhaust pipe 3 into a condenser 40 and changed into liquid refrigerant in the condenser 40, low-pressure refrigerant passing through an expansion device is changed into low-pressure gas in an evaporator 43 and flows into an accumulator 8, the low-pressure gas sucked from a first suction pipe 7A and a second suction pipe 7B connected to the accumulator 8 is compressed into high-pressure gas in a first cylinder 10A and a second cylinder 14B, the high-pressure gas discharged from the first cylinder 10A passes through a first muffler 15B, the high-pressure gas discharged from the second cylinder 14B passes through a second muffler 16B, and the high-pressure gas is merged and then discharged to the inside of the casing 2 to have a high pressure Pd inside the casing 2.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the present disclosure, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" and the like mean that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. The utility model provides a rotary compressor, its characterized in that includes casing, motor, compression mechanism and low-pressure pipeline, the motor is established in the casing and have the bent axle, compression mechanism establishes in the casing and by bent axle drive, compression mechanism includes:

the air cylinder is internally provided with a cylinder chamber and a slide sheet groove;

a piston eccentrically rotating within the cylinder chamber;

the sliding sheet can move in a reciprocating manner in the sliding sheet groove;

the slip sheet control device is connected with the low-pressure pipeline, one end of the slip sheet control device extends into the cylinder chamber and can move back and forth between a first position and a second position according to the pressure difference delta P between the interior of the shell and the interior of the low-pressure pipeline, the slip sheet control device faces the piston and presses the slip sheet so that the slip sheet presses the outer peripheral face of the piston, and the slip sheet control device releases the pressing of the slip sheet on the piston at the second position.

2. The rotary compressor of claim 1, wherein the vane control device is in the first position when the pressure difference Δ Ρ ═ 0; and when the pressure difference delta P is larger than or equal to K, the slide sheet control device is at the second position, wherein K is larger than 0 and is a preset pressure within a preset time after the compression assembly is started.

3. The rotary compressor of claim 2, wherein K is a preset pressure within 30s after the compression assembly is started.

4. The rotary compressor of claim 1, wherein a cross hole is provided on a cylinder block of the cylinder, the cross hole communicating with the cylinder chamber, the vane control device comprising:

the cylinder body part is internally provided with a cavity, the cylinder body part is connected with the machine shell, the cylinder chamber loop is communicated with the cavity, and the cavity is communicated with the transverse hole;

the valve body is arranged in the cavity and can move in the cavity along the length direction of the barrel part;

one end of the central shaft is connected with the valve body, and the other end of the central shaft penetrates through the cylinder body of the air cylinder through the transverse hole to be in contact with and far away from the sliding sheet;

the elastic piece is arranged in the cavity, one end of the elastic piece is connected with the valve body, the other end of the elastic piece is connected with the inner wall surface of the cylinder piece, and the elastic piece has elastic force which presses the valve body towards the piston.

5. The rotary compressor of claim 4, wherein the first end of the cylinder member is open such that one end of the cavity is open, the first end of the cylinder member is connected to the cylinder block through the casing, and one end of the low pressure line communicates with the cavity through the second end of the cylinder member.

6. The rotary compressor of claim 5, wherein the outer peripheral surface of the barrel member is provided with an annular boss adjacent the first end of the barrel member, the annular boss including first and second end surfaces disposed opposite to each other in a length direction of the barrel member, the first end surface of the annular boss being adjacent the first end of the barrel member than the second end surface, the first end surface of the annular boss and the outer peripheral surface of the casing being in abutment with each other.

7. The rotary compressor of claim 4, wherein the other end of the central shaft has a conical tip, the conical tip having a cross-sectional area that gradually decreases in a direction away from the other end of the central shaft.

8. The rotary compressor of claim 4, wherein the outer circumferential profile of the cross section of the center shaft is circular, and the diameter of the center shaft is smaller than the width of the vane abuttable with the center shaft.

9. The rotary compressor according to any one of claims 1 to 8, wherein the crankshaft includes a first eccentric portion, a second eccentric portion, and an intermediate shaft connected between the first and second eccentric portions, the cylinders include a first cylinder having a first cylinder chamber and a first vane groove and a second cylinder having a second cylinder chamber and a second vane groove, a partition plate is provided between the first and second cylinders, the partition plate is provided with a center cavity penetrating the partition plate in an axial direction of the crankshaft, and the intermediate shaft is fitted in the center cavity,

the piston comprises a first piston and a second piston, the first eccentric part is matched in the first piston to drive the first piston to eccentrically rotate in the first cylinder chamber, the second eccentric part is matched in the second piston to drive the second piston to eccentrically rotate in the second cylinder chamber,

the gleitbretter includes first gleitbretter and second gleitbretter, first gleitbretter is in but first gleitbretter inslot reciprocating motion, the second gleitbretter is in but second gleitbretter inslot reciprocating motion, gleitbretter controlling means's one end stretches into in the first cylinder chamber and according to pressure differential delta P can make first gleitbretter presses the outer peripheral face of first piston can relieve first gleitbretter is to the pressing of first piston.

10. A refrigeration cycle system comprising a compressor, a condenser, an expansion valve, an evaporator and an accumulator, wherein the compressor is a rotary compressor according to any one of claims 1 to 9, and a low-pressure line of the rotary compressor is connected to the accumulator.